EP0976948B1 - Dispositif d'amortissement de masses déplacées, en particulier pour systèmes moteurs électromagnétiques - Google Patents

Dispositif d'amortissement de masses déplacées, en particulier pour systèmes moteurs électromagnétiques Download PDF

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Publication number
EP0976948B1
EP0976948B1 EP99114316A EP99114316A EP0976948B1 EP 0976948 B1 EP0976948 B1 EP 0976948B1 EP 99114316 A EP99114316 A EP 99114316A EP 99114316 A EP99114316 A EP 99114316A EP 0976948 B1 EP0976948 B1 EP 0976948B1
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EP
European Patent Office
Prior art keywords
damping piston
damping
hydraulic
moved
pressure chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP99114316A
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German (de)
English (en)
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EP0976948A2 (fr
EP0976948A3 (fr
Inventor
Dieter Maisch
Dieter Tischer
Alfred Trzmiel
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Hilite Germany GmbH
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Hydraulik Ring GmbH
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Publication date
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Publication of EP0976948A2 publication Critical patent/EP0976948A2/fr
Publication of EP0976948A3 publication Critical patent/EP0976948A3/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
    • F16F9/465—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall using servo control, the servo pressure being created by the flow of damping fluid, e.g. controlling pressure in a chamber downstream of a pilot passage

Definitions

  • the invention relates to an arrangement, preferably for electromagnetic valve controls, according to the preamble of claim 1.
  • GB 752 812 shows a complete system intended to check the movement of a piston. It is worked with a single aperture. By mechanically screwing in a screw, the maximum flow is permanently adjusted.
  • GB 2 310 023 describes an exclusively passive vibration damping system, whose application is in automotive vehicle construction.
  • DE 24 19 424 represents a stepped vibration damper for railway wagons whose damping therefore progressively increases because individual holes are gradually closed, and thus the oil is directed over all three valve piston. Again, it is a purely passive system that can not be used in the context of an "electromagnetic drive system".
  • US 3 889 934 shows a hydraulic buffer intended to suppress the swinging of a construction machine arm.
  • the damping device is used in heavy machinery.
  • US 4 937 913 shows a damping element for a door closer.
  • the hydraulic damping takes place via a ball valve.
  • the valve opens suddenly and closes as well.
  • OS 1 271 830 discloses, as the closest prior art, in principle a connection between hydraulic and electrical, which is an electromagnetic actuator.
  • the invention has the object of providing the generic damping device in such a way that it operates quietly, has a long life and reliably slows down to a standstill on the shortest path.
  • damping devices described below are intended for moving masses, preferably for electromagnetic drive systems.
  • electromagnetic drive systems are preferably used for camshaft-free electromagnetic valve controls in internal combustion engines.
  • the arrangement according to FIG. 1 has an electric drive 1 with a housing 2, in which a coil 3 is accommodated. It surrounds a core 4 through which an axis 5 projects, on which an anchor 6 is attached.
  • the armature 6 is advantageously designed as a flat armature. But it can also be cylindrical.
  • the armature 6 is displaceable between the core and a bottom 7 of the housing 2 by means of the axis 5.
  • the armature axis 5 protrudes through the bottom 7.
  • On the outside of the housing 2 located end of the anchor rod 5 sits a spring plate 8, on which a compression spring 9 is supported. It surrounds outside of the housing 2 at a distance the anchor axis 5 and is supported on the outside of the housing bottom 7. Under the force of the compression spring 9, the armature shaft 5 is located on a shaft (not shown) of a valve.
  • the armature axis 5 is axially guided by at least one bearing 10.
  • a housing part 12 is attached, in which is aligned with the armature axis 5, a damping piston 13. It is under the force of at least one return spring 14, which is preferably a plate spring, which requires little installation space, especially in the axial direction.
  • a pressure chamber 15 is provided, into which a Nachsaug Arthur 16 opens. In it sits a check valve 17 which separates the pressure chamber 15 from a reservoir 18 for hydraulic medium.
  • the reservoir 18 is closed by a screw cap 19 which is screwed into the housing part 12.
  • the damping piston 13 is sealed in a bore 20 of the housing part 12 out.
  • the armature shaft 5 is pulled by the compression spring 9 in the stop position in which the armature 6 abuts the housing bottom 7.
  • the damping piston 13 is under the force of the return spring 14 on a housing-side stop surface 21 at.
  • a negative pressure is created in the pressure chamber 15, through which the check valve 17 is opened.
  • the pressure chamber 15 delimiting end face 22 of the damping piston 13 has a cross-sectionally triangular, diametrically extending recess 23.
  • annular channel 25 which is conductively connected via a provided in the housing part 12 bore 26 with the reservoir 18.
  • the control cross section forming a recess 23 passes into the region of the annular channel 25, so that via it and the adjoining bore 26 also hydraulic medium from the reservoir 18 is sucked. Due to the triangular cross-sectional formation of the recess 23, the opening cross-section is steadily increased when pushing back the damping piston 13 in the stop position, so that the pressure chamber 15 is quickly filled with hydraulic medium via both the annular channel 25 and the open check valve 17.
  • Fig. 1a shows the damping piston in the position shown in FIG. 1, in which the coil 3 is de-energized.
  • About the recess 23 in the end face 22 of the damping piston 13 is a connection to the annular channel 25 and the bore 26. If the damping piston 13 is displaced by the armature axis 5 against the force of the return spring 14, the passage cross section between the recess 23 and the annular channel 25 due the triangular cross-sectional formation of the recess steadily smaller.
  • Fig. 1b shows the situation in which the passage cross-section has just become zero. In this position, the damping piston 13 can no longer flow hydraulic medium from the pressure chamber 15 via the recess 23 of the damping piston in the annular space 25.
  • the check valve 17 (FIG.
  • Fig. 2 shows the associated stroke-time characteristic of the device of FIG. 1.
  • the stroke of the armature 6 changes as soon as the electric drive 1 is energized, linear. Since the armature axis 5 initially has a distance from the damping piston 13 (FIG. 1), the armature 6 or the armature axis 5 is displaced with little force. The armature axis 5 passes through a free-flying phase 28 until it encounters the damping piston 13. Then, the armature shaft 5 must move the damping piston 13 against the force of the return spring 14 and the hydraulic pressure.
  • the pressure characteristic is also shown, which results due to the pressure build-up in the pressure chamber 15 (Fig. 1).
  • the pressure begins to rise as soon as the armature axis 5 strikes the damping piston 13. Accordingly, the pressure begins to increase at the moment in which the deceleration 29 begins.
  • the pressure rises within a short time to a maximum value. It is reached just before the displacement of the damping piston 13 is completed. Then, the pressure remains at the high maximum value, which indicates the corresponding hydraulic pressure in the pressure chamber 15, which is established when the damping piston 13 is shifted as shown in FIG. 1c by the armature axis 5 maximum.
  • the damping piston 13 is abruptly moved back under the force of the return spring 14 and the hydraulic pressure built up in the pressure chamber 15.
  • the damping piston 13 takes on the armature axis 5 with the anchor 6.
  • the sliding movement of the armature axis 5 and the armature 6 is supported by the compression spring 9, which, as soon as the damping piston 13 strikes against the stop surface 21 of the housing 1, the armature shaft 5 pushes back into the starting position shown in Fig. 1, in which the armature axis 5 the Distance 27 from the damping piston 13 has.
  • the embodiment of FIG. 3 is formed substantially the same as the previous embodiment.
  • the damping piston 13 is provided in addition to the diametrical recess 23 in the end face 22 with a radially interspersed control cross-section 30 which has rectangular cross-section in the embodiment. It is connected to the pressure chamber 15 via an axially extending bore 31 (FIG. 3 a).
  • a throttle point 32 is provided in the form of an annular gap.
  • the throttle point can also be formed by other suitable structural measures, for example by an additional throttle nozzle.
  • Fig. 3a shows the damping piston 13 in its initial position in which the coil 3 (Fig. 3) is not energized.
  • the armature axis 5 has in this position distance from the damping piston 13.
  • the recess 23 in the damping piston 13 is in communication with the annular channel 25.
  • the armature axis 5 and thus the armature. 6 moved against the force of the compression spring 9.
  • the armature axis 5 strikes the damping piston 13 and carries it along.
  • the passage cross section between the recess 23 and the annular channel 25 is gradually closed with increasing displacement of the damping piston 13.
  • the control cross section 30 partially covers the annular channel 25.
  • the hydraulic medium can escape from the pressure chamber 15 be displaced into the annular channel 25 via the axial bore 31 and the control cross section 30. From here, the hydraulic medium can flow via the bore 26 back to the reservoir 18.
  • the pressure of the hydraulic medium in the pressure chamber 15 decreases almost abruptly within a very short time as soon as the damping piston 23 has reached its end position.
  • the pressure chamber 15 via the axial bore 31, the control cross-section 30, the annular channel 25 and the bore 26 with the reservoir 18 conductively connected.
  • the hydraulic medium can therefore flow into the end position of the damping piston 23 to the reservoir 18.
  • the electromagnetic holding force of the electric drive 1 counteracts only a very small hydraulic counterforce. Due to the relief on the two holes 30, 31 is for holding the armature 6 in the end position with energized coil 3, a much lower magnetic force is necessary than in the embodiment of FIG. 1.
  • the characteristic of the magnet itself can remain unchanged. Up to the maximum of the pressure of the hydraulic medium takes place in the time 35, the pressure build-up, while the pressure reduction is reduced when opening the line connection between the pressure chamber 15 and the reservoir 18 through the holes 30, 31 within the time 36 again.
  • a transmission element 42 is connected to a component 37, which may be an anchor, but may also be any other suitable, for example, hydraulically, pneumatically or mechanically driven element. It is displaceable in a housing part 38 stored. In half the length of the drive element 37 is provided with a radially projecting web 39 which projects through a longitudinal slot 40 in the wall of the housing part 38 and to which the transmission element 42 is attached.
  • the longitudinal slot 40 has a length such that the actuating piston can be moved to the desired extent.
  • On the side opposite the longitudinal slot 40 side of the housing part 12 is provided with a further longitudinal slot 41. As a result, there is a connection between the transfer element 42 receiving space 20 and the surrounding space.
  • a damping piston 13 is provided in each case.
  • the left in Fig. 5 damping piston is formed according to FIG. 1 and the right in Fig. 5 damping piston according to FIG. 3.
  • the two damping pistons can also be formed equal to FIG. 1 or FIG. 3.
  • the associated damping devices are designed accordingly.
  • the transfer element 42 strikes the damping piston 13 after overcoming the free flight path 27. It is then driven against the force of the return spring 14 and the pressure building up in the pressure chamber 15.
  • the pressure build-up and the pressure reduction during displacement of this right in Fig. 5 damping piston 13 take place in the manner as has been explained with reference to FIGS. 3 and 3a to 3c.
  • To the pressure chamber 15 includes a bore 43, in which a check valve 44 is seated.
  • This bore 43 of the pressure chamber 15 is connected to the reservoir 18, which is arranged in contrast to the embodiment of FIG. 3 outside of the housing part 12.
  • the reservoir 18 can of course also, as in the embodiment of FIG. 3, be integrated into the housing part 12.
  • the check valve 44 is seated, as shown in FIG. 3, in such a configuration within the housing part 12 between the pressure chamber 15 and the outside of the housing part 12 located reservoir 18.
  • the check valve 44 ensures as in the previous embodiments that when moving the damping piston thirteenth is closed by the armature axis 5 of the pressure chamber 15 opposite the reservoir 18.
  • the corresponding damping piston 13 is displaced after overcoming the respective free-flight path 27.
  • the longitudinal slot 41 may be provided in the wall of the housing part 12 and a groove.
  • Fig. 6 shows a particularly compact design of the damping device.
  • the housing 2 of the electric drive 1 has an extension 45, in which the compression spring 9 is housed, with which the armature shaft 5 is loaded.
  • the compression spring 9 is supported on the seated on the anchor shaft 5 spring plate 8 and at the bottom of the housing extension 45.
  • the armature shaft 5 abuts against a spring plate 46, which is attached to the free end of the valve stem 47. He is led in a camp 48.
  • the spring plate 46 and a valve spring 47 loading compression spring 49 lie in a receiving space 50 of the housing part 12th
  • the armature 6, which is formed according to the previous embodiments as a flat armature, according to the embodiment of FIG. 5 two free flight paths 27.
  • the damping device 13 is shown only schematically by a dashed line. The design of this damping device 13 will be described in detail with reference to FIGS. 6a to 6c.
  • FIG. 6a shows the damping piston 13 in its middle position, which corresponds to the middle position of the armature 6 according to FIG. 6.
  • the damping piston 13 has two webs 51, 52, with which it is sealed out in the bore 20 of the housing part 12.
  • the two webs 51, 52 each separate two hydraulic chambers 53, 54 and 55, 56 from each other.
  • Both webs 51, 52 are each provided with at least one bore 57, 58 passing through which the pressure chambers 53 and 54 or 55 and 56 are connected to one another.
  • the two adjacent pressure chambers 54 and 55 are separated by a radially inwardly projecting flange 59 of the housing part 12 to which the damping piston 13 bears sealed.
  • the pressure chamber 54 is connected via a bore 60 with an annular channel 61, which is provided in the housing part 12. Via at least one further bore 62 and the hydraulic chamber 55 is connected to the annular channel 61.
  • the damping piston 13 In the position shown in FIG. 6, the damping piston 13 assumes its central position in which the bore 60 is open. The hydraulic medium in the hydraulic chambers 54, 55, in the bores 60, 62 and in the annular channel 61 is thus not under pressure. If now the electric drive 1 (FIG. 6) is actuated and one of its two coils 3 is energized, the damping piston 13 is displaced in the corresponding direction by the armature axis 5, depending on the energized coil 3. If the damping piston 13 is moved from the center position shown in FIG.
  • the annular channel 61 is, as shown schematically in FIGS. 6 and 6a to 6c, connected to the reservoir 18 for the hydraulic medium, which may be disposed within the housing part 12 or outside it.
  • the holes 60, 62 need not have circular cross-section, but may have any other suitable adapted to the particular application cross-section. Instead of the holes 60, 62 and a ring channel is possible.
  • the damping device 13 is, as indicated in Fig. 6 by dotted lines, housed within the electric drive 1 in the receiving space 50.
  • the damping piston 13 is advantageously formed in this case by a part of the armature shaft 5. But the damping piston 13 may also be housed within the electric drive 1, for example in the region of the compression spring 9. In the described embodiment, in contrast to the embodiment of FIG. 5, not air, but hydraulic medium is displaced.
  • Figs. 7 and 7a to 7c show a damper which is similar to the previous embodiment.
  • the damping piston 13 is in turn housed in the receiving space 50, but may for example be arranged in the compression spring 9 receiving housing extension 45.
  • the damping piston 13 is in turn part of the armature axis 5. It carries three spaced apart annular webs 51, 52, 65, of which the two outer annular webs 51, 52 are the same width and wider than the middle annular web 65th
  • Fig. 7a shows the middle or initial position of the damping piston 13.
  • the two outer annular webs 51, 52 each delimit a hydraulic chamber 53, 56 which is bounded on the opposite side in each case by a bearing 66, 67 for the armature axis 5.
  • the two annular webs 51, 52 are each provided with a through hole 57, 58, via which the hydraulic chambers 53, 56 are connected to the hydraulic chambers 54, 55, which are provided between the two outer annular webs 51, 52 and the central annular web 65.
  • the middle annular web 65 is sealingly against the wall of the bore 20.
  • the two hydraulic chambers 53, 56 are connected by at least one bore 60, 62 with the annular channel 61, which is connected to the reservoir 18 for the hydraulic medium.
  • FIGS. 7a to 7c three different positions are shown according to the previous embodiment, when the damping piston 13 moves downwardly from the central position according to FIG. 7a to the valve stem 47 (FIG. 7) in the illustration according to FIG to move down.
  • the corresponding coil 3 of the electric drive 1 is energized, so that the seated on the anchor shaft 5 anchor 6 is moved in the appropriate direction.
  • the damping piston 13 in Fig. 7 down the hydraulic medium is displaced in the manner described with reference to the previous embodiment via the bore 62 into the annular channel 61 and from there via the bore 60 in the hydraulic chamber 53.
  • the passage cross-section is constantly reduced and thus the hydraulic medium in the hydraulic chamber 52 set under increasing pressure.
  • the web 52 finally reaches a position in which it closes the bore 62 with overlap.
  • the hydraulic medium in the now very small hydraulic chamber 56 is pressurized.
  • Via the bore 58 of the web 52 and the hydraulic medium between the two ring lands 52, 65 located in the hydraulic chamber 55 is under the same pressure as in the hydraulic chamber 56. In this position, the deceleration of the damping piston 13 is completed.
  • the damping piston 13 can be moved from the position shown in FIG. 7b further in the position shown in FIG. 7c, in which the bore 62 is opened by the other edge of the annular web 52 again.
  • the hydraulic medium can therefore be displaced from the hydraulic chamber 56 via the bore 58 in the annular web 52, the hydraulic chamber 55 and the bore 62 in the annular channel 61. In this way, the pressure in the hydraulic medium is reduced.
  • the annular web 52 is located at a short distance from the end face 68 of the bearing bush 67.
  • this embodiment is the same as the previous embodiment.
  • the operation is the same as in the embodiment of FIG. 6.
  • the remote from the valve stem 47 end of the armature shaft 5 carries the spring plate 8, on which the compression spring 9 is supported.
  • the two damping pistons 13 are on both sides of the armature 6 and are the same design, but arranged mirror-symmetrically to each other.
  • FIG. 8 and 9 show the armature 6 in its central position in which it is located in the region between the two housing-side stop surfaces 73, 74.
  • the lower damping piston 13 is under the force of the advantageously designed as a plate spring return spring 14 (Fig. 9) on a housing-side locking ring 76 at.
  • the upper damping piston 13 is under the force of the return spring 14 on a housing-side locking ring 77 at.
  • the lower damping piston 13 facing end face 78 projects beyond the stop surface 73.
  • the housing 2 of the electric drive 1 contains the reservoir 18 for the hydraulic medium, which is supplied via two lines 80, 81 to the upper hydraulic chamber 79 in FIG. 9 and to the lower hydraulic chamber 82 in FIG. 9.
  • the two hydraulic chambers 79, 82 are each connected to a housing-side annular channel 83, 84 in connection. In the middle position of the armature 6, the annular channels 83, 84 are connected to the corresponding hydraulic chambers 79, 82.
  • the control cross section designed as an annular channel 83 is reduced by the damping piston 13 and finally closed.
  • the hydraulic medium located in the hydraulic chamber 79 is accordingly set under constantly increasing pressure until the required brake pressure is reached when closing the connection to the annular channel 83.
  • This pressure build-up takes place within the damping stroke DH of the damping piston 13.
  • the damping piston 13 may perform a discharge stroke EH after the damping stroke DH, during which the pressure in the hydraulic chamber 79 is reduced.
  • the annular channel 83 is opened again by the opposite edge 86 of the annular web 93 of the damping piston 13.
  • the hydraulic medium can therefore be displaced from the hydraulic chamber 79 via a bore 85 in the annular channel 83 and from there via the line 80 into the reservoir 18. In this way, the pressure in the hydraulic medium is reduced.
  • the reservoir 18 is, as in the previous embodiments, not fully filled with hydraulic fluid, so that the displaced during the damping stroke DH and the discharge stroke EH hydraulic fluid can be absorbed by the reservoir 18.
  • the electric drive 1 itself in turn has the two coils 3, which are on both sides of the armature 6 with distance from each other.
  • the housing 2 of the electric drive 1 consists of three parts, which are placed on each other and screwed together by screws 89 on a motor block 90 or the like. Due to the multi-part design of the housing 2, the various components can be easily installed and expanded if necessary.
  • a pocket 91 (FIG. 9a) with a T-slot-shaped cutter 92 is incorporated in the connection area.
  • the bag 91 thus sickle-shaped.
  • the shell-side mouth of the bore 85 is formed by an annular groove, so that over the entire circumference of the damping piston 13 during the discharge stroke EH, the hydraulic medium in the manner described can be displaced from the hydraulic chamber 79 in the housing-side annular channel 83.
  • the pressure spring 49 loading the valve stem 47 and the pressure spring 9 loading the armature axis 5 have the same spring characteristics (FIG. 10). As a result, the middle position of the armature 6 shown in FIGS. 8 and 9 is achieved when the electric drive 1 is not energized.
  • the compression springs 9, 49 may also have different c-values, but must be dimensioned so that the center position of the armature 6 can be adjusted.
  • Fig. 10 the spring characteristics of the two compression springs 9, 49 and the resulting differential force are shown.
  • the two spring characteristics run in opposite directions to each other. If one of the two damping pistons 13 is displaced in the manner described, then adds to the differential force as soon as the annular channel 83 and 84 is closed, according to the pressure build-up in the hydraulic chamber 79 and 82, an additional force (damping stroke DH).
  • the magnetic force of the electromagnet 1 must be greater than the sum of differential force and superimposed damping force.
  • the described and illustrated electric drive 1 can be used in the form of the electromagnet.
  • Other actuators can be used which operate pneumatically, electrically, mechanically, piezoelectrically and the like.
  • Fig. 11 shows an example of the effect of the damping device when closing and opening a valve of a motor vehicle. In the left half of the behavior is shown without damper, in the right half using the damper described. If the valves work without damper, then abrupt movements occur both when closing and when the valve is fully opened. When using the damping device, however, the transition to closing or opening of the valve is continuous and continuous, which is indicated in Fig. 11 each by dash-dotted circles.
  • Fig. 12 shows exemplary valve control cycles at different engine speeds. Depending on the speed of the engine, a different number of damping processes is required within given times, each of which takes place within the same time.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (12)

  1. Dispositif,
    qui comprend un système d'entraînement de préférence électromagnétique, en particulier pour des commandes de soupape électromagnétiques sans arbres à came dans des moteurs à combustion, avec une masse à déplacer (5, 6, 47, 75, 37, 42) et au moins un élément d'amortissement qui exerce une force opposée à la masse à déplacer (5, 6, 47, 75, 37, 42) et qui est un piston amortisseur (13),
    qui délimite une chambre de pression (15, 54, 55, 79, 82), caractérisé en ce qu'au moins une conduite hydraulique (25, 60, 62, 80, 81) débouche dans la chambre de pression (15, 54, 55, 79, 82),
    conduite qui lors du coulissement du piston amortisseur (13) le long d'une trajectoire de coulissement peut être fermée par la masse à déplacer (5, 6, 47, 75, 37, 42) par refoulement du fluide hydraulique hors de la chambre de pression (15, 54, 55, 79, 82) et par génération d'une pression hydraulique dans la chambre de pression de sorte que la pression hydraulique augmente avec la trajectoire croissante du piston amortisseur (13),
    en ce que la masse à déplacer (5, 6, 47, 75, 37, 42) est à une certaine distance (27) du piston amortisseur (13) dans une position de départ de sorte que le dispositif présente une course libre dans la zone dans laquelle seule une faible force est nécessaire au début pour le déplacement de la masse à déplacer (5, 6, 47, 75, 37, 42),
    et en ce que la masse à déplacer (5, 6, 47, 75, 37, 42) fait impact après avoir surmonté la course libre sur le piston amortisseur (13), lors du déplacement duquel une section transversale d'écoulement de la conduite hydraulique (25, 60, 62, 80, 81) pour le fluide hydraulique peut être réduite en permanence pour amener le fluide hydraulique de la chambre de pression (15, 54, 55, 79, 82) dans la conduite hydraulique (25, 60, 62, 80, 81).
  2. Dispositif selon la revendication 1,
    caractérisé en ce que le piston amortisseur (13) présente dans sa face avant (22) délimitant la chambre de pression (15) et/ou un carter (2) au moins un renfoncement (23) avec une section transversale s'élargissant de préférence en direction de la face avant (22) du piston amortisseur (13) par l'intermédiaire duquel une connexion peut être établie entre la chambre de pression (15) et la conduite hydraulique (25).
  3. Dispositif selon l'une quelconque des revendications 1 à 2,
    caractérisé en ce que la conduite hydraulique (25, 60, 62, 80, 81) est reliée à un réservoir (18) de fluide hydraulique.
  4. Dispositif selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce que le piston amortisseur (13) présente au moins une section transversale de commande (30) qui le traverse transversalement à son axe et qui est prévue à distance de sa face avant (22) délimitant la chambre de pression (15) et en ce que de manière avantageuse, la section transversale de commande (30) peut être reliée à la conduite hydraulique (25) dès que le piston amortisseur (13) est déplacé au-delà de sa position fermant la conduite hydraulique (25).
  5. Dispositif selon la revendication 4,
    caractérisé en ce que la conduite hydraulique (25) est reliée à au moins un point d'étranglement (32) qui est de manière avantageuse une fente annulaire pratiquée entre le piston amortisseur (13) et la paroi (24) d'une chambre de logement (20) du piston amortisseur (13).
  6. Dispositif selon l'une quelconque des revendications 1 à 5,
    caractérisé en ce que pour l'amortissement de la masse à déplacer (37, 42, 5, 6, 47, 75) dans les deux directions, il est prévu respectivement un piston amortisseur (13) chargé de manière avantageuse par ressort à l'encontre de la masse à déplacer (5, 6, 47, 75, 37, 42), lesdits pistons étant disposés de préférence symétriquement l'un par rapport à l'autre.
  7. Dispositif selon l'une quelconque des revendications 1 à 6,
    caractérisé en ce que le piston amortisseur (13) présente au moins deux arcades annulaires (51, 52) qui séparent respectivement deux chambres de pression (53 à 56) et en ce que les deux arcades annulaires (51, 52) présentent de préférence respectivement au moins une ouverture (57, 58) permettant de relier entre elles les chambres de pression (53, 54, 55, 56) voisines.
  8. Dispositif selon la revendication 7,
    caractérisé en ce que le piston amortisseur (13) présente une autre arcade annulaire (65) qui se trouve entre les deux autres arcades annulaires (51, 52) et sépare deux chambres de pression (54, 55) voisines.
  9. Dispositif selon l'une quelconque des revendications 1 à 8,
    caractérisé en ce que le système d'entraînement est un entraînement électrique (1) et en ce que le piston amortisseur (13) fait partie de l'axe d'ancrage (5) de l'entraînement électrique (1).
  10. Dispositif selon l'une quelconque des revendications 1 à 8,
    caractérisé en ce que le système d'entraînement est un entraînement électrique (1) et en ce que le piston amortisseur (13) est disposé de façon coulissante sur l'axe d'ancrage (5) de l'entraînement électrique (1).
  11. Dispositif selon l'une quelconque des revendications 1 à 10,
    caractérisé en ce que le piston amortisseur (13) présente un alésage (85) qui débouche dans la face avant du piston amortisseur (13) délimitant la chambre de pression (79, 82) et dans la surface d'enveloppe de cette dernière.
  12. Dispositif selon l'une quelconque des revendications 1 à 11,
    caractérisé en ce que la masse à déplacer (5, 6, 47, 75) fait impact sur le piston amortisseur (13) après avoir traversé la course libre (27, FF) et l'entraîne à l'encontre de la force de ressort et de la pression hydraulique en exécutant une course d'amortissement (DH) du piston d'amortissement (13) et en ce qu'après avoir traversé la course d'amortissement, la masse à déplacer (5, 6, 47, 75) entraîne de préférence le piston amortisseur (13) en exécutant une course de décharge (EH) au cours de laquelle la pression chute dans la chambre de pression (15, 79, 82).
EP99114316A 1998-07-31 1999-07-21 Dispositif d'amortissement de masses déplacées, en particulier pour systèmes moteurs électromagnétiques Expired - Lifetime EP0976948B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19834522A DE19834522A1 (de) 1998-07-31 1998-07-31 Dämpfungseinrichtung für bewegte Massen, vorzugsweise für elektromagnetische Antriebssysteme
DE19834522 1998-07-31

Publications (3)

Publication Number Publication Date
EP0976948A2 EP0976948A2 (fr) 2000-02-02
EP0976948A3 EP0976948A3 (fr) 2002-12-04
EP0976948B1 true EP0976948B1 (fr) 2006-09-20

Family

ID=7875953

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99114316A Expired - Lifetime EP0976948B1 (fr) 1998-07-31 1999-07-21 Dispositif d'amortissement de masses déplacées, en particulier pour systèmes moteurs électromagnétiques

Country Status (3)

Country Link
US (1) US6205964B1 (fr)
EP (1) EP0976948B1 (fr)
DE (2) DE19834522A1 (fr)

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* Cited by examiner, † Cited by third party
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US6776391B1 (en) 1999-11-16 2004-08-17 Continental Teves Ag & Co. Ohg Electromagnet valve
DE10016600A1 (de) * 1999-11-16 2001-05-17 Continental Teves Ag & Co Ohg Elektromagnetventil
US6592095B2 (en) * 2001-04-09 2003-07-15 Delphi Technologies, Inc. Electromagnetic valve motion control
US6681730B1 (en) * 2002-08-27 2004-01-27 Ford Global Technologies, Llc Hydraulic damper for an electromechanical valve
US6675751B1 (en) 2003-03-12 2004-01-13 Ford Global Technologies, Inc. Two-mass bi-directional hydraulic damper
DE10314860A1 (de) * 2003-04-02 2004-10-14 Bayerische Motoren Werke Ag Elektrischer Ventiltrieb für Verbrennungsmotoren mit Ventilspieldämpfungselement
US6896236B2 (en) * 2003-06-02 2005-05-24 Ford Global Technologies, Llc Controlled leakage hydraulic damper
CN101057085A (zh) * 2004-09-10 2007-10-17 丹福斯有限公司 弹簧以及结合这种弹簧的阀
EP1805441B1 (fr) * 2004-09-10 2010-01-20 Danfoss A/S Electrovanne a dispositif amortisseur

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GB752812A (en) * 1953-10-28 1956-07-18 Nat Pneumatic Co Inc Improvements in or relating to buffer devices for pressure-fluid actuated pistons
DE1293897B (de) * 1962-06-07 1969-04-30 Spuhr & Co M Elektromagnetisch betaetigte Stellvorrichtung fuer ein Ventil
US3889934A (en) * 1973-12-19 1975-06-17 Houdaille Industries Inc Hydraulic buffer
DE2419424A1 (de) * 1974-04-23 1975-11-06 Deutsche Bundesbahn Schwingungsdaempfer fuer laufwerke von fahrzeugen
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US6116570A (en) * 1998-03-30 2000-09-12 Siemens Automotive Corporation Electromagnetic actuator with internal oil system and improved hydraulic lash adjuster

Also Published As

Publication number Publication date
EP0976948A2 (fr) 2000-02-02
DE19834522A1 (de) 2000-02-03
US6205964B1 (en) 2001-03-27
DE59913854D1 (de) 2006-11-02
EP0976948A3 (fr) 2002-12-04

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